Accounting machine



1945- w. H. ROBERTSON ET AL 2,369,252

ACCOUNTING MACHINE Filed Sept. 25, 1941 10 Sheets-Sheet 1 Add FIG.-1 i 94 9;

Williefin H. Robertson and Willis E. Eickman Inventors By @QAL 'W Their Attorney Feb. 13, 1945. w H ROBERTSON ETAL 2,369,252

ACCOUNTING MACHINE Fil ed Sept. 25, 1941 I0 Sheets-Sheet 2 William H. Robertson and Willis E. Eickman Inventors Their Attorney Feb. 13, 1945. w. H. ROBERTSON ETAL I 2,369,252

ACCOUNTING MACHINE Filed Sept. 25, 1941 10 Sheets-Sheet 3 William H. Robertson and Willis E. Eickman Inventors Their Attorney Feb- 1945- w. H. ROBERTSON ETAL 2,369,252

ACCOUNTING MACHINE Filed Sept. 25, 1941 10 Sheets-Sheet 4 H54KAF'7 William H. Robertson and Willis E. Eickman Inventors Their Attorney Feb. 13, 1945. w. H. ROBERTSON ETAL 2,369,252

ACCOUNTING MACHINE Fiied Sept. 25, 1941 10 Sheets-Sheet 5 242 l I and 242 F|2G 6 Z34 ,.)Z40

w/hp/ 2;J w 24 245 g 7 w 225 Willi H. Robertson zz Y and His E. Eickman Inventors 26/ BYQMLM Their Attorney Feb. 1-3, 1945. w. H. ROBERTSON ET AL 2,369,252

ACCOUNTING MACHINE Filed Sept. 25, 1941 10 Sheets-Sheet 6 William H. Robertson and Willis E. Eickman Inventors Their Attorney Feb. 13, 1945. w. H. ROBERTSON ET AL 2,369,252

' ACCOUNTING MACHINE Filed Sept. 25, 1941 10 Sheets-Sheet '7 William H. Robertson and Willis E. Eickman Inventors Their Attorney 1945- w. H. ROBERTSON ET AL 2,369,252

ACCOUNTING MACHINE Filed Sept. 25, 1941 10 Sheets-Sheet 8 William H. Robertson and Willis E. Eickman Inventors Their Attorney FIG.2 4% 28 1945- w. H. ROBERTSON ETAL 2,369,252

ACCOUNTING MACHINE Filed Sept. 25, 1941 10 Sheets-Sheet 9 5 far/7 0 01/5 5a y Tofu I I William H. Robertson and Willis E. Eickman Inventors Their Attorney 1945' w. H. ROBERTSON ET AL 2,369,252

ACCOUNTING MACHINE Filed Sept. 25, 1941 10 Sheets-Sheet 10 William H. Robertson and Willis E. Eickman l nventors B MW w #ET as mm mm s E mm Sh min k 53 Gun mmm IIIIIII\ Q\ MR 265 b n k NEW 3% PE a Em k. SE

m at MM: RM n56 kmmnEE Em Dim ENGEE ER 3 2Q 56 n t mulmfi fi 355% $5 wzSE a R565 QNMVE Their Attorney Patented Feb. 13, 1945 ACCOUNTING MACHINE William H. Robertson and Willis E. Eickman, Dayton, Ohio, assignors to The National Cash Register Company, Dayton, Ohio, a corporation of Maryland Application September 25, 1941, Serial No. 412,346

14 Claims.

) 2'7, 1938, to Charles H. Arnold, and No. 2,176,561,

issued October 1'7, 1939, to Everett H. Placke.

The present invention is directed to the incorporation of four totalizer lines, each supporting a maximum I of ten sets of interspersed totalizer wheels, in machines of the general type referred to above. This provides a machine having a maximum of 40 individual totals for the accumulation and the storing of the various items marketed by various merchandising establishments.

A machine of the character referred to above is admirably adapted for the analyzing of the sales of wholesale merchandising establishments and in its present embodiment is arranged for use by a wholesale meat merchant or packing house for the keeping of a complete analysis of the sales of the meat products marketed thereby. However, it is not the desire or intention to limit the machine of this invention to the use outlined above, as with minor alterations it may be arranged for use in connection with numerous other types of businesses.

One object of the present invention is to provide a machine of the character referred to above with a plurality of lines of interspersed totalizers.

Another object is to provide a machine of the character referred to above with four lines of intersp'ersed totalizer sets.

Still another object is to supply means to control the selection of the various totalizer lines for engaging and disengaging movement.

A further object is to provide means to impart engaging and disengaging movement to the selected totalizer lines.

Another object of this invention is to furnish means to select the various sets of totalizers on the various totalizer lines for engagement with the totalizer actuators.

A further object is the provision of novel means in transaction'and total control keys and feeler mechanisms cooperating witli'said selecting disks, to select the different totalizer lines for engaging and disengaging movement, and to provide means eifective in total-recording operations to impart an auxiliary movement to the selecting disks tocause totals to be transferred from one totalizer to another.

Another object is the provision of means under the control of the total selecting disk for disabling the selecting disk feeler mechanisms in totalrecording or resetting operations to cause the selected totalizer to remain in a cleared condition.

Another object is to provide a machine having a plurality of totalizer lines, each supporting a plurality of sets of totalizers, with a selecting disk for each totalizer line and a selecting disk common to all the totalizer lines, said disks positioned by corresponding transaction and total control keys and havingcooperating therewith a feeler mechanism for each totalizer line to select said lines for engaging and disengaging movement, said selecting disk common to all the totalizer lines normally efiective to render all the feeler mechanisms ineffective, except the feeler mechanism for the totalizer being cleared, and effective, after said totalizer is cleared, to render all the feeler mechanisms ineffective, except the one for the totalizer to which the total is being transferred.

With these and incidental objects in view, the invention includes certain novel features of construction and combinations of parts, the essential elements of which are set forth in appended claims and a preferred form or embodiment of which is hereinafter described with reference to the drawings which accompany and form a part of this specification.

In said drawings:

Fig. 1 is an elevation of the right-hand side of the machine, showing in particular a portion of the total control'mechanism.

Fig. 2 is a cross-sectional view taken just to the right of one of the amount banks and showing the differential mechanism associated with 7 said amount bank, and the four totalizer lines.

Fig. 3 is a detail view of the tens transfer mech anism for the amount bank shown in Fig. 2.

Fig. 4 is a cross-sectional'view of the machine, taken immediately to the right of one of the transaction banks, showing in particular the differential mechanism associated with said transaction bank, and the mechanism controlled by said differential mechanism for shifting the corresponding totalizer line laterally to select the different sets of totalizer wheels thereon for en gagement with the amount actuators.

Fig. is a diagrammatic front elevation of a portion of the machine, showing in particular the mechanism for shifting the #1 totalizer line laterally to select the different sets of totalizer wheels thereon for engagement with the amount actuators.

Fig. 6 is a right side elevation of the cam mechanism for shifting the four totalizer lines a slight distance laterally to aline the selected set of totalizer wheels with the tens transfer mechanism.

Fig. 7 is a detail view of the mechanism for disabling the transfer shifting mechanism in total-recording operations.

Figs. '8, 9, 10, and 11 show, respectively, detail plan views of a part of the selecting disk feeler mechanisms for the Nos. 1, -2, 3, and 4 rows of transaction keys and the corresponding totalizer lines.

Fig. 12 is a right side elevation showing the mechanism for imparting engaging and disenimparting feeling movement to the feeler mechanisms.

Fig. 16 is a plan view of the feeler mechanism for the #1 row of transaction keys.

Fig. 1'7 is a right side elevation of the feeler mechanisms and shows in particular the means for disabling the feeler mechanisms in total-recording operations. 7

Fig. 18 is a perspective view of the feeler mechanism for the #1 row of transaction keys.

Fig. 19 is a detail view of the total selecting disk and a portion of the positioning mechanism associated therewith.

Fig. 20 is a detail view of a portion of the mechanism associated with the transaction differential mechanism shown in Fig. 4, for shifting the #1 totalizr line laterally.

Fig. 21 is a detail view of the aliner for alining the #1 totalizer line in selected positions.

Fig. 22 is a diagrammatic plan view of a portion of the keyboard of the machine embodying the instant invention.

Figs. 23, 24, 25, and 26 are detail views of the selecting disks for the four rows of transaction keys.

Fig. 2'] is a detail view of the selecting disk for the total keys.

Fig. 28 is a time chart giving in graphic form the timing of the important mechanisms of the machine embodying the instant invention.

GENERAL DzscRIP'rIoN The keyboard of the machine embodying the instant invention comprises a plurality of rows of amount keys which in adding operations control the positioning of corresponding amount differential mechanisms, said differential mechanisms in turn being arranged to transmit the values of the depressed amount keys. to the printing mechanism and to the wheels of the selected totalizer. In sub-total or total-recording operations, the amount differential mechanisms, which include an amount actuator for each denominational order, are positioned by the wheels of the selected totalizer in accordance with the amount standing on said totalizer wheels, said differential mechanisms in turn transmitting such positioning to the printing mechanism in the usual manner. i

Instead of the conventional three lines of totalizers, the present machine is provided with four lines of totalizers, each supporting a maximum of ten sets of interspersed totaiizer wheels, which wheels are engageable with the amount actuators of the differential mechanisms for actuation thereby. The four lines of interspersed totalizers are located around the amount actuators, as is the usual custom, and each of said totalizer lines is mounted in a framework which is shiftable laterally to aline the different sets of totalizer wheels with the amount actuators, and is also shiftable radially to engage and disengage the selected set of wheels with and from said actuators.

Four rows of transaction keys, corresponding to the four totalizer lines, are provided for controlling the lateral shifting of the corresponding totalizer frameworks to aline the various sets of totalizer wheels with the amount actuators. The four rows of transaction keys likewise control the positioning of four corresponding add selecting disks, which, in cooperation with their respective feeler mechanisms, control the radial shifting movement of the framework for the corresponding totalizer lines to cause the selected set oftotalizer wheels on the selected totalizer line to be engaged with and disengaged from the amount actuators.

The amount diiferential mechanisms are driven by a main cam shaft, which shaft in adding operations, makes one revolution. In sub-total recording or reading operations, and in total-recording or resetting operations, the main cam shaft makes two such revolutions. Adding operations, which require one revolution of the main cam shaft, are commonly referred to as one-cycle operations, and sub-total and totalrecording operations, which require two revolutions of the cam shaft, are commonly referred to as two-cycle operations.

In adding operations, initial movement of the differential mechanisms, under influence of the cam shaft, causes said mechanisms to be positioned under control of the depressed amount keys, and, during this positioning, the framework of the selected totalizer line is shifted laterally, under influence of the depressed transaction keys, to aline the selected set of totalizer wheels thereon with the amount actuators. After the selected set of totalizer wheels has been alined with the amount actuators, the corresponding feeler mechanism, in cooperation with the corresponding selecting disk, which has previously been positioned under influence of the depressed transaction key, causes the totalizer engaging mechanism to be connected to the shiftable framework for the selected totalizer line. Operation of the totalizer engaging mechanism causes the selected set of totalizer wheels to be engaged with the amount actuators after said actuators have been positioned by the amount keys, as explained above, and return movement of said actuators, under influence of the main cam shaft, rotates the selected totalizer wheels in accordance with the values of said depressed amount keys to add in saidiwheels the amount set up on the keyboard.

The resent machine is provided with four total contro' keys corresponding to the four lines of totalizers, and said keys control the positioning of a corresponding selecting disk which is common to all four totalizer lines and which, in cooperation with the feeler mechanisms for said lines, controls the engaging and disengaging movements of said lines in sub-total and totalrecording operations. In sub-total and total-recording operations, the transaction keys are used in-conjunction with the total control keys to control the lateral shifting of the totalizer frameworksv to select the different sets of totalizers supported thereby for engagement with the amount actuators. The lateral shifting of the totalizer frameworks, under influence of the effective transaction key, occurs during the first revolution of the main cam shaft or during the first cycle of sub-total and total-recording operations,

- and during this first cycle the amount differential mechanisms are retained in zero position.

Near the end of the first cycle of a total-recording operation, the wheels of the selected totalizer are engaged with the amount actuators, and initial movement of said actuators, during the first part of the second cycle of such operation, rotates said wheels in a reverse direction until a long tooth thereon stops said wheels in zero position. This positions the amount actuators and the printing mechanism in accordance with the amount standing on the selected set of totalizer wheels, and, prior to return movement of said actuators, the framework for the selected totalizer line receives disengaging movement to movement, in the second cycle of such operation,

and consequently said wheels are restored to their original positions, after which the totalizer framework receives disengaging movement to disengage said wheels from said actuators.

A novel tens transfer mechanism, which functions in adding operations, is provided for transferring tens digits from lower to higher denominations. In adding operations, when the wheels of the selected totalizer pass from 9 to while being rotated in an additive direction by the amount actuators, a long tooth on said wheels trips the transfer mechanism for the next higher order. After the amount actuators have com pleted their return movement, the framework for the selected totalizer line receives an auxiliary lateral shifting movement to move the selected set of totalizer wheels out of alinement with the amount actuators and into alinement with a series of transfer segments which are located adjacent to the corresponding amount actuators, there being one such transfer segment in each denominational order of each of the four totalizer lines except the lowest order. After the selected totalizer wheels are engaged with the transfer segments, said segments are released to the driving action of their springs, to cause the tripped segments to advance the wheels of the next higher order one digit, to effect a tens transfer.

The selected set of totalizer wheels remains in alinement with the transfer segments at the end of the machine operation, and are shifted back intoalinement with the amount actuators at the beginning of the succeeding operation, at which time all the previously tripped transfer segments are restored to untripped position.

. lected totalizer line to be shifted radially in adding time. When the control lever is moved to read" position, it functions in cooperation with the transaction keys and the four total control keys to cause the framework for the selected totalizer line to be shifted radially in sub-total orreading time. When the total lever is moved to "reset" position, it functions in conjunction with the ttransaction keys and the four total control keys to cause the framework for the selected totalizer line to be shifted radially in total or reset time.

One of the novel features of the machine embodying the present invention is that it is arranged to transfer totals from one set of totalizers Y to another, and said machine is presently constructed to transfer totals into certain of the sets of totalizer wheels on the #4 totalizer line from certain of the sets of totalizer wheels on any of the other three totalizer lines. However, this system of transferring totals is simply a matter of choice, as the machine may be arranged to transi fer totals into the sets of totalizer wheels on any of the other totalizer lines by the simple expedient of properly altering the selecting disks. Also, the machine is presently arranged to transfer totals only in total-recording or resetting operations,and this likewise is a matter of choice.

The first part of a transfer total operation is the same as any total-recording or resetting operation; that is, in the first cycle of such operation, the amount actuators are retained in zero position, and the framework for the totalizer line corresponding to the depressed transaction key and the depressed total control key is shifted laterally to aline the set of Wheels on said line corresponding to said depressed transaction key with said amount actuators. Near the end of the first cycle of transfer total operations, the set of wheels selected for clearing is engaged with the amount actuators, and initial movement of said actuators, during the second cycle of such operation, reversely rotates said selected wheels to zero in the manner explained in connection with total and sub-total recording operations. Near the end of the first cycle of transfer total operations, and after the totalizer set from which the total isto be cleared has been selected, the selecting dsks are given an auxiliary movement, Which places them in new positions. Said disks then, in cooperation with the feeler mechanisms, cause the totalizer set on the #4 totalizer line corresponding to the depressed transaction key in the fourth transaction row to be engaged with the amount actuators after said actuators have been positioned by the wheels of the totalizer set from which the total i being transferred, as explained above. Return move ment of the amount actuators, near the end of the second cycle of the transfer total operation, causes the amount cleared fromthe selected set of totalizer wheels on the Nos. 1, 2, or 3 totalizer lines to be added into or transferred to the seleeted set of wheels on the #4 totalizer line.

In sub-total recording or reading operations, the mechanism for selecting thetotalizers on the #4 totaiizer line for the transferring of totals is rendered. inoperative.

In the ensuing detailed description, mechanism ertinent to the instant invention will be described in detail. However, mechanism of a standard nature, which has become fully established in the art, will be but briefly described, as reference may be had to the aforementioned patents for a full disclosure of this standard mechanism.

Drruuo DESCRIPTION Framework and operating mechanism The machine embodying the instant invention has right and left main frames 50,. only the right frame here shown (Figs. 1, 5,-12, and 14), and right and left sub-frames only the right subframe here shown, said frames being secured to a machine base 52, which, to ether with various cross frames. bars, and rods, holds' the frames 50 and 5| in fixed relationship toeach other. The mechanism of the machine is' enclosed in a suitable cabinet or case 53 (Figs. 1 and 2), which is in turn secured to the machine base 52. The cabinet 53 is provided with suitable closures, through which access may be had to the important mechanisms of the machine. If desired, these closures may be provided with locks to prevent unauthorized persons from having access to said important mechanisms.

Under normal conditions, the machine is operated by an electric motor of conventional design, such as those used in previous machines of this type, said motor being released for operation by the use of the usual starting bar I03, located on the right-hand side of the machine. In addition to the electric motor, a hand crank (not shown) Is provided for operating the machine manually when there is a failure in the electric current or when such current is not available.

Keyboard By referring to Fig. 22, which is a diagrammatic view of the keyboard of the machine of this invention, it will be seen that the keyboard comprises a plurality of rows of amount keys 54 (only three rows here shown) for controlling the positioning of the corresponding amount actuators in adding operations, four rows of transaction keys numbered 55 to 90 inclusive for controlling the selection of the different totalizers on the four totalizer lines, and four total control keys SI to 94 inclusive for use in conjunction with the transaction keys for controlling the selection and the engaging and disengaging movements of the four totalizer lines in sub-total recording or reading and total-recording or resetting operations.

A total control lever 95 (Figs. 1 and 22), which is manually positionable to three positionsnamely, add, "read, and resetis provided for controlling the add, read, and reset functions of the machine. A key 95 is used for operating a cylinder type lock mounted in the total control lever 95, said lock having a projection 91, which, in cooperation with three notches 98 corresponding to the three positions of said total control lever 35, looks said lever in any of its positions.

' said lever, which notches, in cooperation with a spring-pulled alining pawl I01, yieidingly retain said lever 55 in any of its three positions.

Amount diflerentials As previously explained, the amount keys 54 (Figs. 2, 5, and 22) control the positioning of corresponding amount differential or actuator mechanisms, and, inasmuch as this differential mechanism is substantially duplicated in each denominational order, it is believed that a description of the mechanism of one such denominational order, as shown in Fig. 2, will be sufficient for the purpose of this specification.

The amount keys 54 (Fig. 2) of the denominational row here shown, which is representative of all the rows of amount keys, are mounted in a framework I00 supported by rods MI and H0 in turn supported by the main framework of the machine. Depression of any one of the amount keys 54 rocks a zero stop pawl I02 counter-clockwise out of the path 'of a projection I03 of an amount actuator I04 free on a shaft I05 iournaled in the main frames 50, and moves the lower end of said depressed key into th path of said projection I03. When no amount key 54 is depressed, the zero stop pawl I02, under influence of a spring I09, is retained in the path of the projection I03 and breaks the latch for this amount bank in zero position, as will be explained later. A,

The actuator I04 (Fig. 2) has therein an angular camming slot III, through which extends a stud I I2 in a latch II3 pivoted on a stud I I4 carried by a latch arm I I5 free on the shaft I05. The stud H2 also extends through an angular cammin slot H6, which is a companion slot to the slot III, said slot II5 being in a differential balance plate III free on the shaft I05. A footshaped extension of the latch II3 has thereon a shoulder IIB, which, in cooperation with a similar shoulder on a latch driving segment II9 free on the shaft I05, forms a driving connection between said segment and the latch arm HE. A link I20 operatively connects the driving segment II! to an operating lever I2I pivoted on a stud I22 in a partition plate I23 for this particular amount bank, there being such a partition plate for each amount bank.

A boring in a downward extension of the lever I-2I freely engages a rod I24, opposite ends of which are secured in similar arms I25 (only the left-hand arm being shown here) said arms being pivoted on studs (not shown) similar to and in axial alinement with the stud I22, said studs being secured in their corresponding partition plates I23. Each of the arms I25 carries a set of rollers I26 and I21, which cooperate, respectively, with their corresponding set of companion plate cams I28 and I29 (only one set here shown), secured on a main cam shaft I30 journaled in the main framework of the machine.

A clutch mechanism, not here shown but well known in the art, operatively connects the main cam shaft I30 to the operating motor, said motor, as previously explained, arranged to drive the shaft I30 one clockwise revolution in adding operations and two such revolutions in reading and resetting operations. Revolution of the main cam shaft I30, by means of the cams I28 and I29, imparts an invariable oscillating movement to the arms I25, the lever I2I, and the latch-operating segment H9, first clockwise and then counterthe projection I03 to break the latch H3 in zeroclockwise, according to the time given in space I of the time chart, Fig. 28.

Initial movement clockwise of the segment H9, by means of the shoulder thereon in cooperation with the shoulder H8 on the latch I I3, carries said latch and the latch arm H clockwise in unison therewith. The latch H3, by means of the stud H2 in cooperation with the slots III and II 6, carries the actuator I04 and the balance plate H1 clockwise in unison therewith. In this case, a spring I61 and the downward inertia of the balance plate H1 cause the slot H0, in cooperation with the stud I I2, to retain the latch in engagement with the segment I I9 and thereby overcome any tendency of the slot I H in the actuator I04 to cam said latch I I3 out of en-' gagement with the shoulder on the. operating segment H9. The actuator I04 moves in unison the corresponding one of a series of alining Y notches I32 in a curved alining bar I33 secured to the partition plate I23 for this particular amount bank, said plate I23 being supported by the shaft I05 and the rods- I34, I35, and I30, in turn supported by the main framework of the machine. As the segment H9 continues its clockwise movement without interruption, an arcuate surface thereon passes in the path of the footshaped extension of the latch H3 to lock said latch, the arm H5, and the actuator I04 in set positions.

The actuator I 04 has, on the periphery thereof, a plurality of gear teeth I31 arranged to cooperate with the different sets of totalizer wheels I38 to I inclusive, carried respectively by the Nos. 1, 2, 3, and 4 totalizer lines. a

In adding operations, after the actuator I04 has been positioned, as explained above the selected totalizer line is shifted radially to engage the corresponding one of the selected set of totalizer wheels thereon with the teeth l31,of the actuator I04. After the corresponding one of the selected set of totalizer wheels has. been engaged with the actuator I04, return movement counter-clockwise of the operating segment H9 moves the arcuate surface on said segment beyond the foot-shaped extension of the latch I I3 and simultaneously causes a stud I42 carried thereby to engage a raised surface on the latch arm H5 to return said arm and, through the stud I I2 and the slots III and H6, the actuator I 04 and the balance plate H1 counter-clockwise in unison therewith. Counter-clockwise movement of the latch arm H5 causes the alining notch I32, in cooperation with the arcuate surface I3I and the spring I61, to reengage the shoulder H8 on said latch H3 with the corresponding shoulder on the operating segment H9. movement counter-clockwise, the actuator I04 rotates the wheel I38 of the selected totalizer in an additive direction, in accordance With'the' During its return position in the well-known manner. Also during the first revolution of the shaft I30, the selected totalizer line is shifted laterally to aline the corresponding one of the selected set of wheels thereon with the actuator I04, as will be explained later. After the selected totalizer wheel has been alined with the actuator I04, the totalizer line is shifted radially or inwardly to engage said wheel with said actuator I04 prior to its initial movement clockwise, which movement reversely 1 rotates said wheel until a lon tooth thereon comes into contact with a stop which locates said wheel in zero position and positions the actuator I04 in accordance with the amount standing on said wheel.

In resetting or total-recording operations,' the selected totalizer heel is disengaged from the actuator I04 prioryto its return movement countar-clockwise, and consequently'said wheel remains in a zeroized condition. In reading or sub-total recording operations, the selected totalizer wheel remains in engagement with the actuator I04 during its return movement counter-clockwise and consequently is restoredto its original position.

An aliner I43 (Fig. 2), in cooperation with the teeth I31, retains the actuator I 04 in set position in all types of operations. Obviously the aliner I43 is disengaged while the actuator I04 is being positioned.

The differential positioning of the actuator I 04, under influence of the amount keys 54 in adding operations, and under influence of the corresponding totalizer wheel in reading and resetting operations, is transmitted to the printing mechanism by the well-known beam mechanism, which will now be described.

The latch arm H5 carries a stud I44 upon which is pivoted a beam I45 having a slot in the rearward end thereof, which cooperates with a stud I-48 in a link I41, the upper end of which is pivotally connected to a gear sector I48 free on a shaft I49 journaled in the machine framework. The lower end of the link I41 is pivoted to a segment I50 free on a shaft I5I journaled in the main-framework, and said segment I50 is operatively connected by a link I52 to a companion gear sector I53 free on a shaft I54 also journaled in the main framework. The gear sector I53 meshes with the external teeth of an external-internal printer drive gear I55, the internal teeth of which bear on the periphery of a disk I56 fast on a shaft I51 supported by the printer framework. The external teeth of the gear I55 mesh with and drive a type wheel I58 for this particular denomination, said ty'pe wheel being free on a shaft I59 journaled in the printer framework. The internal teeth of the gear I55 mesh with a pinion I50 (Fig. 2) in turn meshing with a similar pinion I'Iii on a square shaft I62 journaled in borings in the disks I55, said shaft I62 being operatively connected, by a similar gearing, to other type wheels for this particular order, said type wheels adapted to print in the various columns of multi-column record material.

The internal-external gear mechanism for driving type wheels is fully disclosed in United States Patent No. 1,693,279, issued November 27, 1928, to Walter J. Kreider, to which reference may be had for a more complete description thereof.

When the lever I2I (Fig. 2) nears the terminus of its initial movement clockwise, a roller I63 carried thereby engages a rounded surface I04 ln-curved surface on the upper edge thereof into engagement with a bushing on the shaft I65, to cause said beam, through the medium of the link 1, to position the sector I48, the segment Ill, and the sector III in accordance with the value of the depressed amount key in adding operations, and in accordance with the amount 'on the selected totalizer wheel in reading and/or resetting operations. The sector I53, through the medium of the external-internal gear I55, ositions the type wheel I58 in accordance with the positioning of the actuator I65. An aliner I65, secured on a shaft I66 journaled in the main framework of the machine, cooperates with alining teeth on the gear sector I46 to aline said sector and the mechanism connected thereto by the link II] in set positions.

Transfer mechanism A tens transfer mechanism is provided for transferring tens digits from lower to higher denominations. The transfer mechanism for each totalizer line comprises a transfer segment and its associated tripping mechanism for each deset up on th amount keys in the selected totalizer wheels, it is necessary to shift the selected totaliaer line or lines a slight distance laterally to aline said wheels with the corresponding transfer segments. Immediately thereafter, the previously tripped transfer segments function to add one in the totalizer wheels of the next higher orders.

During the auxiliary shifting of the totalizer line to move the selected totalizer wheels into alinement with the transfer segments, said line is partially disengaged to insure that said wheels do not stumble on the transfer segments and to insure that adjacent wheels do not stumble on the teeth of the actuators. The selected totalizer wheels remain in engagement with the transfer segments at the end of machine operation and are disengaged therefrom immediately at the beginning of the succeeding operation, after which the totalizer line is restored laterally to aline the wheels thereof with the amount actuators.

Inasmuch as the transfer mechanisms for the diflerent denominational orders and for the different lines of totalizers are identical, it is believed that a description of the transfer mechanism for the denominational order of the #1 totalizer line, shown in Fig. 2, will suffice.

The transfer mechanism for the denominational order of the #1 totalizer line, shown in Fig. 2, comprises a transfer segment I16 (Fig. 8) pivoted on a stud I1I in a plate I12 supported by the rods I34, I35, and I36. A spring I13 urges the segment I16 counter-clockwise to normally maintain a camming surface Ill thereon in engagement with a stud I15 in a transfer operating arm I16 free on a stud I11 in the plate I12. A spring I16 urges the arm I16 clockwise to normally maintain a bent-over ear I19 thereon in contact with a retaining tooth I86 on a transfer trip yoke I8l free on a stud I62 in the plate I12 for the order here shown.

aseaasa on the lower edge of the beam I45 and forces an When the selected #1 totalizer wheel I86, in the next lower-order to the order shown in Figs. 2 and 3, passes through 'zero, a long tooth I68 thereon engages a bent-over extension I84 on the yoke I8I and rocks said yoke counter-clockwise to disengage the tooth I86 from the ear I19 to release the arm I16 to the action of the spring I18, which rocks said arm a slight distance clockwise until the ear I16 passes beyond the tooth I86 and until 9. depending finger I65 of said arm I18 contacts a stud I66, which at this time is in the position here shown in dot-and-dash lines. The stud I86 is secured in a restoring disk I61 fast on the shaft I65, there being such a disk for each denominational order, with the exception of the lowest order. Also fast on the shaft I65 (Fig. 3) is a crank I88 carrying a stud I69 embraced by a slot in a cam lever I96 free on a ltl-tionary stud I9I. Angularly disposed arms of t e lever I96 carry, respectively, rollers I92 and I88, which cooperate respectively with the peripheries of companion plate cams I94 and I95 secured on the main cam shaft I66.

The timing of the cams I96 and I 95 is given in space 6 of the time chart, Fig. 28, from which it will be seen that initial movement of said cams. through the lever I96, rocks the disk I81 clockwise, causing the stud I86, in cooperation with the depending finger I85, to restore the operating ,movexnents, to enter the value of the amount arm I16 counter-clockwise against the action of its spring I18 until the ear I19 passes beyond the tooth I86. Continued rotation of the cams I94 and I returns the disk I81 and the stud I66 a slight distance counter-clockwise to permit the ear I19 to engage the tooth I86 to latch the transfer mechanism in untripped position, and to po sitlon the stud I86 a slight distance away from the finger I65, as shown in dot-and-dash lines in Fig. 3. Restoring movement counter-clockwise of the operating arm I16 causes the stud I15, in cooperation with the camming surface I14, to restore the tripping'segment I16 clockwise against the action of the spring I13.

It will be noted that the restoring of the transfer mechanism takes place during initial movement of the amount actuators I64 and prior to the time the selected totalizer wheels are engaged therewith. Return movement of the amount actuator for the next lower order wheel I98 (Fig. 3) rotates said wheel in an additiv or clockwise direction, causing the long tooth I63 thereon to engage the extension I64 to trip the yoke I6I, in the manner explained above. After the amount actuator has completed its return movement, the transfer shift is imparted to the #1 totalizer line to move the wheels I36 of the selected totalizer into alinement with the transfer segments I16, and immediately thereafter the cams I94 and I95 return the disk I81 counter-clockwise to the position shown here. The operating arm I16 moves clockwise in unison with the disk I81, causing the stud I15, in cooperation with the camming surface I14, to permit the spring I16 to rock the segment counter-clockwise to advance the totalizer wheel I36, for the order here shown, one digit toeifect a tens transfer.

The mechanism for imparting auxiliary or transfer shifting movement to the totalizer line will be explained later herein in connection with the totalizer selecting and engaging mechanism.

In reading and resetting operations, the wheel I38 (Fig. 3) is reversely rotated by the amount actuator I 64, in the manner explained above, until the long tooth I83 thereon comes in contact with the extension I66 to locate said wheel The differential mechanism for each of the four rows of transaction keys is similar in every respect to the amount differential mechanism shown in Fig. 2 and explained above, and, as the trans- 10 action differential mechanism is substantially duplicated. for each row of transaction keys, it is believed that a description of the differential mechanism for the first row of transaction keys, shows in Fig. 4, will suflice for all.

- The transaction keys 55 to 63 for the first transaction bank are mounted in a key frame I98 supported by the rods I I and I I0 in exactly the same manner as the amount key banks. Depression of any one of the transaction keys 55 to 63 rocks a zero stop pawl I99'c0unter-clockwlse out of the path of a projection 200 of an actuator 20I free on the shaft I05, said actuator 20I being operatively connected to a balance plate 202 by means of angular slots in said actuator and said plate, in cooperation with a stud in a latch 203 pivotally mounted on a latch arm 204 free on the shaft I05. The latch 203 cooperates with a shoulder on a differential operating segment 205 free on the shaft I05 and connected by a link 206 to an operating lever 20'! free on a stationary stud 208.

The cam lever 201 carries rollers 209 and 2I0,

which cooperate, respectively, with the peripheries of companion plate cams 2H and 2I2' secured on the main cam shaft I30. The cams 2H and 2I2 function according to the time given in space I of the time chart (Fig. 28) to rock the actuator 20I first clockwise and back to normal positionduring each revolution of said main' shaft I30.

The parts of the transaction differential described briefly above are similar to and function exactly like similar parts of the amount actuator shown in Fig. 2 and described earlier herein.

Initial movement clockwise of the lever 201, through the segment 205 and the latch 203, carries the actuator. 20I clockwise in unison therewith until the projection 200 contacts the stem of the depressed transaction key, which positions said actuator according to the value of said depressed transaction key. This disengages the latch 203 from the segment 205 in exactly the same manner as described for theamount bank, thus permitting said segment and the lever 201 to complete their initial movements clockwise independently thereof. When the lever 20! nears the terminus of its initial movement clockwise, a roller 2I3 carried thereby engages an arcuate surface on a beam 2I4 pivoted on the arm 204, to position said beam in accordanc with the depressed transaction key. The rearward end of the beam 2I4 is bifurcated to embrace a stud 2I5 in a link 2I6, the upper end of which link is pivotally connected to a gear sector 2II secured to one of a plurality of nested tubes 2 I8 free on the shaft I49. The lower end of the link 2I6 is pivotally connected to a segment 2I9 free on the shaft I5I, and connected by a sleev 220 to a crank 22I. The crank 22I (Figs. 4, 5., and 20) is connected by a link 222 to a segment 223 free on the shaft I05, said segment meshing with a gear 224 secured on a short shaft 225 Journaled in plates 226 and 221 supported by the rods I34, I35, and I36 (Fig.2).

Also secured on the shaft 226 (Figs. 5 and is a disk 228 'carryingthree studs 229 which freely engage corresponding borings in the lefthand face of a drum cam 230 fre on the shaft 225. The cam 230 has a helical cam groove 23I which cooperates with a roller 232 secured in a slide 233 shiftably mounted on the top surfac of a yoke 234 by means of studs in said slide in cooperation with horizontal slots in said yoke, said roller 232 arranged to extend through one of said horizontal slots. The yoke 234 is free on the shaft 225, but is held against rotary movement by a roller 235 carried thereby, in cooperation with a horizontal slot in a bracket 236 s'ecured to the plate 226, and by means of a vertical slot in the left-hand extension thereof, in

cooperation with a stud 231 in the plate 221. An annular groove 238 (Fig. 5) in a reduced portion of the drum cam 230, in cooperation with a slotted bracket 239 secured to the yoke 234, maintains said drum cam and said yoke in fixed lateral relationship to each other.

An upturned portion of the slide 233 (Figs. 5 and 20) has therein a, slot 240 which engages an annular groove MI in a hub portion of a totalizer frame side member 242, said hub portion having therein a boring which freely engages a shaft 243 which is arranged to be shifted radially in a manner presently to be described to engage the selected set of totalizer wheels with the amount actuators. The side member 242 supports the right-hand end of the #1 totalizer line or rod, while a similar side member 258 .(Fig. 2), also slidably mounted on the shaft 243, supports the left-hand end of said #1 totalizer line, said side members, together with the #1 totalizer line L and the shaft 243, forming a shiftable framework for engaging and disengaging the #1 totalizer wheels with and from the amount actuators. The lower ends of the side members 242 and 258 have therein similar slots which engage similar toothshaped blocks 244 carried by the plates I23, said -blocks being the shape of and in alinement with the teeth in the actuators I84 (Fig. 2).

The roller 235 (Figs. 5, 6, and 7) extends into a cam groove I244 in one of four camming extensions on a transfer shift cam 245 free on the shaft I05. An extension 246 of the cam 245 has pivotally connected thereto the upper end of a link 24'! having a stud 249 in the lower end, which normally engages a slot in an arm 248 fixedly connected, by a hub free on a/stud 250 in the plate 226, to a cam arm 25I. The cam arm 25I carries rollers 252'and 253, which cooperate respectively with the peripheries of companion 235, shifts the yoke 234 toward the left, as viewed in Fig. 5,- which movement is transmitted by the bracket 239 to the drum cam 230 and thence by the cam groove 23I and the roller 232 to the slide 233. This shifts the member 242 and the #1 totalizer framework a slight distance toward the left to move the selected totalizer wheels out of alinement with the transfer segments I I0 and into alinement with the amount actuators I84 (see also Figs. 2 and 3).

After the selected set of wheels on the #1 totalizer has been shifted out of alinment with the transfer segments, as explained above, the roller 2l3 (Fig. 4) engages the beam 214 to'position said beam in accordance with the depressed.

transaction key, and this positioning is transmitted by the link .2l8 to the sector 2n, the segment H8, and the crank 22!. The crank 22l, by means of the link 222, rocks the gear segment 222 from zero position, as here shown, in a clockwise direction to a position corresponding to the depressed transaction key. Clockwise movement of the segment 223 (Figs. 4 and 5) rotates the gear 224, the shaft 225, and the drum cam 238'counterclockwise, causing the cam groove 2 in said drum cam, in cooperation with the roller 222, to shift the slide 222 and the totalizer framework, comprising the members 242 and 258 and the #1 totalizer line, toward the left, as here viewed,

to aline the set of totalizer wheels I88 corresponding to the depressed transaction key 88 to 88 with the amount actuators I84.

In adding operations, after the selected set of totalizer wheels has thus been alined with the amount actuators, radial shifting movement is imparted to the shaft 243 (Figs. 2 and 5), as will be presently explained, to engage the selected totalizer wheels with the amount actuators I84, after said actuators have been positioned .-under influence of the depressed amount keys. Return movement counter-clockwise of said actuators rotates said wheels in an additive direction to enter the amount therein, and, after said actuators have completed their return movements, the totalizer wheels are slightly disengaged from the actuators, and the cams 254 and 258 (Figs. 5 and 6 and space 2 of the time chart, Fig. 28) function to shift the #1 totalizer a slight distance to the right to move the selected set of wheels thereon into alinement with the transfer segments I18. After this, the #1 totalizer line is returned to full engaged position and the tripped transfer segments I18 (Fig. 3) then function, under influence of their cams I84 and I98 (space 3, Fig. 28), to effect the transferof tens digits from lower to higher denominations, in the manner explained earlier herein.

At the end of a machine operation, the selected set of totalizer wheels remains in alinement with the transfer segments I18 and is returned into alinement with the amount actuators I84 at the beginning of the succeeding operation.

In reading and/or resetting operations, the mechanism for the #1 transaction bank, shown in Fig. 4 and explained above, functions exactly the same as in adding operations, toialine the selected set of totalizer wheels with the amount actuators during the first cycle of said reading and/or resetting operations. However, the engaging movement of the #1 totalizer line is different, in that the selected totalizer wheels thereon remain in engagement with the amount actuators at the beginning of the second cycle of such operations, and said actuators, in their initial movement, reversely rotate the selected totalizer wheels to zero, in th manner explained previously.

The other three totalizer lines are shifted laterally, for the selection of the different sets of totalizer wheels thereon and for the transfer of tens digits, by mechanism similar to and functioning in exactly the same manner as the mechanism for the #1 totalizer line.

action keys, which diflerential mechanism, in

Totalizer line selecting and engaging mechanisms The difierential mechanisms for the four rows of transaction keys (Fig. 22), in addition to selecting the sets of totalizer wheels corresponding to said keys for engagement with the amount actuators, likewise control the positioning of corresponding selecting disks 288 to 282 inclusive (Figs. 23 to 26) ,which disks, in cooperation with their feeler mechanisms, control the selection of the corresponding totalizer lines for engaging and disengaging movement and also control the selection of other totalizer lines, having a set of group total wheels in the zero positions thereof, for engaging and disengaging movement, so that a group total of the items being entered in the different transaction rows may be obtained.

Likewise, the four total keys M to 84 (Fig. 22) have a differential mechanism similar to that explained in connection with the #1 row of transreading and resetting operations, controls the positioning of a corresponding selecting disk 282 (Fig. 27), which, in cooperation with the feeler mechanisms, causes the totalizer line corresponding to the depressed total key to be selected for engaging and disengaging movement. In resetting operations, the disk 283 and associated mechanism cause the #4 totalizer line to receive engaging and disengaging movement in adding time, as will be explained later, to cause the totals being cleared from the totalizers on the #1, #2, or #3 totalizer lines to be transferred to the sets of wheels on said #4 totalizer line corresponding to the depressed transaction keys 88 to 8.

Referring now to Fig. 4, positioning of the sector 2" by the differential mechanism for the first row of transaction keys is transmitted by the tube 2l8, to a crank 284 (Figs. 5 and 14), which crank is secured on the right-hand end of said tube. vA link 288 connects the crank 284 to a bell crank 268 .free on the shaft 188, and said bell crank has a, slot 281 through which extends a stud 288 in on end of a link 289, the other end of which link is pivotally connected to an arm 218 secured to a sleeve 2' in turn secured in the arms of a yoked member 212, said sleeve 2' being free on a shaft 213 journaled in the machine framework. The stud 288 extends through the link 288 and into a camming slot 214 in the selecting disk 288 for the first transaction bank, and said stud forms a driving medium between the bell crank288 and said selecting disk.

The stud 288 remains in the position shown in Fig. 14 in adding and reading operations; however, in resetting operations, said stud is shifted upwardly, in a manner to be described later, to impart an auxiliary movement to the selecting disk 259 for the transferring of totals.

The tube 218, the crank 284, the link 285, the bell crank 268, and the stud 288 form an operating connection between the first transaction bank differential mechanism and the selecting disk 259. Consequently, said disk is positioned in accordance with the depressed transaction key. A similar mechanism is provided for transmitting the positionin of the differential mechanisms for the second, third, and fourth rows of transaction keys to their corresponding selecting disks 268, 28!, and 282 (Figs. 23, 24, and 25). Likewise, a similar mechanism is provided, for transmitting the positioning of the difierentlal mechanism for the total keys 8| to 84 (Fig. 22) to the total selecting disk 263, said mechanism including one of the tubes 2l3 (Figs. and 19) and its integral crank 255. A link 215 connects the crank 255 to a bell crank 216 free on the shaft I05 and having a slot engaged by a stud 211 in one end of a link 218, the other end of which link is connected to an arm 219 secured to the sleeve Ill. The stud 211 also engages a slot 251 m the total selecting disk 253. The parts described above for positioning the total selecting disk 263 are similar to and function exactly like the corresponding parts for the first transaction bank, shown in Fig. 14 and described earlier. As previously explained, in adding operations the differential mechanism for the total keys ul to :14 (Fig. 22) remains in zero position and, when in said position, locates the total selecting disk 263 as shown in Figs. 19 and 27.

In adding operations, after the transaction selecting disks have been positioned under influence of the transaction keys, the feeler mechanism functions to select the totalizer line corresponding to the depressed transaction key for engaging and disengaging movement. I

The feeler mechanism for the #1 totalizer line (Figs. 8, 14, 16, 17, and 18) comprises feeler bars 280 and 28!, which extend acrossthe selecting disks 259 to 263 inclusive, each of said bars connecting two similar arms free on a shaft 282 carried by a #1 totalizer engaging yoke 283 free on a rod 2%. The rod 284 is carried by a yoked member 235 pivoted on trunnions 28c and 281 secured, respectively, in the frame 5| and a partition plate 238 (Fig. 16) supported by the rods B32, B35, and 836. Downward extensions of the feeler bars 280 and 28f (Figs. 14, 1'7, and 18) have similar locking slots therein, said slots being in reverse relationship to each other, through which extends a stud 283 in the upper end of a link 2913, the lower end of which link is pivoted to a lever can free on a stud 292 fast in the frame St. A spring 233 urges the lever 29! clockwise to normally maintain an extension thereof in contact with a stud 29 3 in an operating spider 295 free on the shaft 5%. The spider 235 (Fig. 15) has a slot which engages a stud 295' in one arm of a yoked cam lever 291 free on a stud 298 in the frame 56. Another arm of the lever 29l carries a roller 292, which cooperates with a cam groove tilt in a cam. till secured on the main cam shaft itii, I

Revolution clockwise of the cam 3m rocks the spider 2% first counter-clockwise and back to normal position, according to the time given in space t of the time chart, Fig. 28. Initial movement counter-clockwise of the spider 295 (Figs. 15 and .17) withdraws the stud 294 from the extension of the lever 29! to release said lever to the action of the spring 233. However, in adding operations, the total selecting disk 263 (Figs. 19 and 27) is so positioned that a high portion of a control slot 322 therein is opposite a roller 303 carried by the lever 2%. Consequently, such clockwise movement of said lever is obstructed, and as a result the stud 289 remains in the locking portions of the slots in the arms of the feelers 233 and 283 (Figs. 17 and 18) to lock said feelers in fixed relationship to each other. When a low portion of the control slot 302 (Figs. 19 and 27) is opposite the roller 303, clockwise movement of the lever 295, under influence of the Spring 293, shifts the link 290 and the stud 289 downwardly to move said stud into clearance portions of the inoperative to select the #1 totalizer line for engaging and disengaging movement.

By referring to mg. 15, it Will be seen that the yoke 285 has an extension carrying a stud 303, which engages a slot in one leg of the spider we. Consequently, movement of said spider rocks the yoke zoo first clockwise and back to normal position, according to the time given in space 4 of the chart, Fig. 28. The trunnions 285 and 231 form a fulcrum point for said yoke 235 (Figs. 16 and 15). initial movement clockwise of the yoke 235 (Figs. 14, 16, 1'7, and 18), by means of the rod 284, carries the yoke 283 downwardly in .unison therewith, and said yoke :83, by means of the shaft 282, in turn carries the feelers 280 and 28! downwardly, to cause said feelers to feel the periphery of the selecting disks. By observing Figs. 8' and 16, it will be seen that the feeler 28l is undercut so that it cooperates only with the total selecting disk 263, while the feeler 280 cooperates With the peripheries of all the selecting disks, including the transaction disk and the total selecting disk. I

By referring to Fig. 27, it will be noted that, when the total selecting disk 263 is in adding position, a high portion 301 of the periphery thereof is always opposite the feeler 28! to obstruct downward movement of said feelerl In this particular type of feeling mechanism, two high points are required, one opposite each of the feelers 280 and 28!, to select, and, conversely, only one low point opposite either of said feelers 280 and 28l to reject.

Depression of any one of the keys to 33 (Figs. 22 and 26) in the first transaction bank positions the selecting disk 259 for this bank, so that the one of a series of high points 308 thereon corresponding to the depressed key is opposite the feeler 280 to block downward movement of said feeler. Inasmuch as downward movement of the other feeler 1.3! is always blocked in adding operations, downward movement of said feelers and the shaft 2152 (Figs. 16 and i8) is obstructed, causing said shaft 282 to become the fulcrum point for the yoke 283. Continued clockwise movement of the yoke 285 (Figs. 16, 17, and 18) causes the yoke 283 to be rocked in a clockwise direction also.

An extension of the yoke 283 (Figs. 5, l2, l7, and 18) has therein an opening 309, which 'cooperates with a stud 3i!) in a link 3 pivotally connected to the lower end of a lever 312 free on a stud m in the frame 5|. A link 3i4 pivotally connects the lever 3I2 to the upper end of a lever locking slots in the arms of the feelers 280 and 28!, to disconnect said feelers so that they will be M5 secured on the shaft 243, said lever carrying a roller 3R6, which engages a camming slot 3H in a totalizer engaging plate 3i8 secured to the frame 51. A tenon on the end of the shaft 243 rotatably supports a roller 3L9, which engages a radial slot 320 in the plate (H8. The left-hand end of the shaft 243 supports a roller, similar to the roller 3H3, which cooperates with a radial slot in a left-hand engaging plate similar to the plate 3l8, said plate having a cammin-g slot, similar to the slot 3, which cooperates with a roller carried by a crank secured on the left-hand end of the shaft 243, such engaging mechanism for the left-hand end of the shaft 243 not being shown here.

A spring 321 (Fi 12) urges the link 3 clockwise to normally maintain a stud 322, carried thereby, in engagement with a downward branch of an L-shaped slot 323 in the frame 5|. The stud 322 is normally locked in the downward branch of theslot 323 by an arcuate surface 324 on one a hub 32! free on the shaft I33. The hub 32! (Figs. 5, 12, and 13) has therein aclutch out, which engages corresponding tenons on a similar hub 323 also free on the shaft I35 and having integral therewith a crank 323. The crank 323 pivotally supports theupper end of an engaging link 333 having in the lower end thereof a stud 33l. which cooperates with a slot in an arm 332 secured to a hub 333 free on a stationary stud 334. Also secured to the hub 333 is a cam lever 336 carrying rollers 333 and 331, which cooperate respectively with companion plate cams 333 and 333 secured to the main shaft I33. The cams 333 and 333 drive the spider 326 in adding operations,

and the.-stud 33l is maintained in engagement with the slot in the arm 332 in such operations by the bifurcated lower end of a .bell crank 343 free on a stationary stud 34! and having a slotted extension which engages a stud 342 in a lever 343 secured to the shaft 213. A camming slot 344 in the lever 343 engages a stud 346 in a crank 346 secured to the right-hand end of a zero throwout shaft 341 journaled in the machine framework.

In adding operations, no movement is imparted to the zero throwout shaft 341. Consequently, said shaft and the parts secured thereon remain in the positions shown in Fig. 12, to cause the bell crank 340 to retain the stud 33l in engage-.

notch 343, in said extension, in alinement with said stud 3l3. Immediately after the notch 343 has been alined with the stud 3), the cam 36! (Fig. 15) causes the feeler mechanism to function, as explained above, to rock the yoke 233 clockwise to cause the opening 333 (Figs. 12 and 18), in cooperation with the stud 3l3, to lift said stud into engagement with the notch 343.

It will be noted by referring to space 2 of the timechart, Fig. 28, that the cams 254 and 26! (Figs. 5 and 6) have shifted the #1 totalizer wheels out of cooperative alinement with the transfer segments and into cooperative alinement with the amount actuators, and that the differential mechanism for the first transaction bank has operated the drum cam 233 to aline the selected set of wheels on the #1 totalizer line with said amount actuators prior to functioning of the feeler mechanism, the timing of which is given in space 4, Fig. 28. After the amount actuators have been positioned under influence of the depressed amount keys, and after the #1 totalizer line has been shifted laterally to aline the selected set of wheels thereon with said actuators, the spider 326 (Fig. 12) is returned clockwise to shift the link 3 rearwardly to rock the lever 3l2 counter-clockwise, which movement, by means of the link 3l4, rocks the lever 3l5 and the shaft 243 also in a counter-clockwise direction. Counter-clockwise movement of the lever 3l6 causes the roller M6, in cooperation with the camming slot 3", to shift the shaft 243 and the totalizer framework, including said shaft, the side members 242 and 263, and the #1 totalizer line (Figs. 2 and 5), downwardly to engage the selected set of wheels with the amount actuators leg of a totalizer engaging spider 323 integral with I34. The totalizer framework is guided in its engaging and disengaging movements by the rollers 3l3 in cooperation with the radial slots 323, and by the slotted ends of the side member 242 and 253 in cooperation with the blocks 244.

Mechanism actuated by initial or engaging movement of the #1 totalizer framework, including the shaft 243 (Figs. 5 and 21), is provided for alining and locking the cam 23!) i selected position to insure that the selected set of totalizer wheels remains in accurate alinement with the amount actuators and transfer segments. Initial downward movement of the shaft 243, under influence of the mechanism shown in Fig. 12 and explained above, causes said shaft, in cooperation with a camming groove 4 in a locking pawl 4l2 free on a stud M3 in the plate 226, to rock said pawl counter-clockwise.

Counter-clockwise movement of the pawl 412 engages a tooth 4l4 thereon with one of a series of tooth spaces in a gear 5 on the shaft 225, to aline said shaft and to secure said shaft and the drum cam 233 against further rotary movement, after they have been positioned under influence of the depressed key in the #1 transaction row. to insure that the selected set of wheels on the #1 totalizer line will remain in accurate alinement with the amount actuators and the transfer segments.

After the-selected set of totalizer wheels has been engaged with the amount actuators, return movement of said actuators rotates said wheels in an additive direction to add therein the amount set up on the amount keys.

After the amount has been added in the selected set of totalizer wheels, the cams 333 and 333 (Fig. 12 and space 5, Fig. 28) return the spider 326 a slight distance counter-clockwise to partially disengage the totalizer wheels from the amount actuators. During this partial disengagement, the cams 254 and 255 (Fig. 6 and space 2, Fig. 28) function to shift the selected set of totalizer wheels into cooperative alinement with the transfer segments, after which the spider 323 is returned clockwise to engage said selected totalizer wheels with said transfer segments. The transfer mechanism then functions in the manner explained earlier herein to effect the tens transfer.

It will be noted that, when the feeler mechanism, including the yoke 283 (Figs. 12 and 18),

lifts the stud 310 into engagement with the notch 348,.the stud 322 in the link 3 is simultaneously lifted out of the downward branch of the slot 323 and into alinement with a substantially horizontal branch of said slot, which horizontal branch, in cooperation with said stud, retains the stud 3") in engagement with the notch 343 during engaging and disengaging movement of the totalizer framework.

At the end of machine operations, the engaging spider 326 remains in the position shown in Fig. 12; consequently, the #1 totalizer line remains in engaged position at the end of machine operation. At the beginning of the succeeding operation and prior to initial movement of the actuators, the spider 326 returns the stud 3M, the link 3| l, and associated parts forwardly to impart disengaging movement to the #1 totalizer line; and, when the stud 322 arrives opposite the downward branch of the slot 323, the spring 32l immediately disengages the stud 3) from the notch 343 and engages said stud 322 with said downward branch, as shown in Fig. 12. The 

